Adjustment device, particularly for the cross-slides of grinding machines



1,813,165 THE 3 Sheets-Sheet 1 July 7, 1931. JUNG ADJUSTMENT DEVICE, PARTICULARLY FOR CROSS SLIDES OF GRINDING MACHINES Filed March 8, 1928 t .lllllu w m lll-lll-l-II I I'" lllll IPP W/ F .70 V90 30/ L far? 1709' 6 1 l M atz or/zey Jul 7, 1931. K. JUNG 1,813,165

ADJUSTMENT DEVICE, PARTICULARLY FOR THE CROSS SLIDES 0F GRINDING MACHINES Filed March 8, 1928 3 Sheets-Sheet 2 l L@ L\ \X\\ X\\\ Z\\ i |ll\ IIIIIIIIIIA ocney July 7, 1931. K. JUNG 1,813,165

' ADJUSTMENT DEVICE, PARTICULARLY FOR THE CROSS SLIDES OF GRINDING MACHINES I Filed March 8, 1928 3 Sheets-Sheet 3 I 1/? ve/zi or fad 7. 4/29 Patented July 7, 1931 UNITED STATES PATENT- OFFICE KARL JUNG, F BERLIN, GERMANY ADJUSTMENT DEVICE, rAnrIcULAnLY FOR THE cnoss-smnns or GRINDING mcH NEs a Application filed March 8, 1928, Serial No.

In machine tools, especially grinding machines, which possess a tool or work-piece car 'rying slide moved longitudinally backwards and forwards and also a cross-slide serving for carrying out the adjustment movement, precaution is takento carry out the control of the cross-slide either by hand, for the purpose of the adjustment, or automatically. In the'latter case the driving mechanism controlling the cross-slide is controlled by the longitudinal slide, which at the end of one or at'the end of a. number of backwards and forwards movements strikes against-a stop or the like, which efiects the adjustment control.

In all these automatic controls the adjustment is always therefore dependent upon the movement of the longitudinal slide.

Now in the mass production-art precaution is taken to estimate the working time required for a piece of work, according to the size of shaving to be taken'o'fi' and according to the number of revolutions and the diameter of the grinding disc employed. The result of this is that the estimated working time differs considerably from the time actually. required for-the work. f

The present invention has for its object to obviate, this disadvantage .and't0 efi'ectthe finished treatment of a work piece independ- 30 ently of the arrangement of the machine', and the longitudinal movement simply upon the basis of the calculation undertaken. I 'In the drawings is illustrated an embodia ment of the invention by way ofexample and in which 1 Fig. 1 is a front viewof a machine constructed according to the invention and shows the following arrangement.

Fig.2 is a side View of from the right-hand of'Fig. '1.

' Figs. 3-7 show the special construction of the controlling of the cross-slide in'a larger. scale, namely, Fig. 3 is a cross sectionthrough, the cross-slide of'the machine; Fig. 41s a] line'4-4; Fig. 5 is a section through Fig. 31 in the directionof the line 5--5.-; Fig, 6' is a 1 section through Fig. 3 inthe direction of'the line 6 6 Fig. 7 isa section through ,Fig. 4; in the direction of the line ..,7 and- The shaft 260,043, and. in Germany March 5, 1927.

Fig. 8 is a diagrammatic View showingthe entire system of connections, the controlling valves and pumps. I In the drawings 1 is either the stationary table of-a grinding machine, or, as in the example illustrated in Figs. 1 and 2, the movable longitudinal slide upon the frame'A of a grinding machine. On the frame'A is also mounted the. bearing77 in which the spindle 78 for holding the work pieceis journalled. The crossslide 6 is located in a horizontal direction upon the part 1. In the slide is mounted a shaft 7 upon which is located a driving pulleyi 8, which by means of a belt 9 a pulley 82- afiixed on a shaft'70 mounted in a bearing 71 arranged uponv the slide6. On the shaft the grinding disk or the workpiece to be treated is arranged. I prefer, as shown in the drawings, to arrange; the inding disk? 2 on said shaft 70. is driven by means of 'a' belt 7 3 from a pulley 7 4 arrangedon a shaft-7 5. The latter has fixed on it a pulley '7 6 which may be driven in any suitable manner by means of a motor or the like; From the shaft 7 by means of worm gearinglQ and worm. and pinion gearing'll and 12 is driven a shaft 13,- which drives two oil pumps 14 and lS-(Figs; 1 and 8). The pressurelead 16 of the pump 14 extends toathrottle'valve or throttle cook 17 and to a'recessin which 'a shaft 18 may rotate. This shaft, at theposition at which the lead 16' emergesinto'its recess, as may be seen es ecially from Figure 2, isconstructed' in the orm of a three-way cock. Inthe position of this. cock illustrated in Fig. .4 the lead V 16 connectedto a lead 21- 6) by means I of thelead 19 and the upwardly directed the machineseen lead 20,-which vemerges,fnea'rq.to.one end of b.

a cylinder 22, inwhich a piston-.23 is slidably mounted backwards and forwards. L At'the' other end of the cylinder emerges a" lead which, by e n -bfen-surw y ii' ed 45 section through F is. 3in'the direction of the; lead 25531111 3 f iv 1adi'26 bl t ng 5 therefrom,.leadslto thejotherlside of the shaft 1.8, wherefr'omiit-egiteiidsby -meansof a lead i 27 to an oil;- collecting chamber 83 ifrjomwh'ieh p mp=1a u1a ttl'e' cock ;17"i's, as'may-be-observed' from Figure 7 hollow built, and the bore extending therethrough is in communication with an inner hollow region. The hollow region is covered at the top by means of a ball 28, which is pressed against the opening by a spring 29, so that this throttle cock functions simultaneously as a safety Valve. The rotation of the cock may take place by means of a hand lever 30.

The second pump 15 feeds, through a lead 31 to which is attached an upwardly directed vertical lead 32, into a cylinder 33, in which moves a valve 34 upon the rod of which are located two pistons 35 and 36. In the position of the valve 34 illustrated in Figure 6 this valve resides with its left side against the appropriate seating. The lead 32 consequently is in communication, by means of the cylinder space, with a lead 37, which leads into a cylindrical chamber 38. A rotary piston turns within the chamber 38. The chamber is divided into two sections by means of thepiston and a partition wall 40. From the second section a lead 41 extends towards the other side of the valve 34. The two sides of the valve are furthermore connected to the oil container by means of leads 42 or 43, moreover from the two chambers extend leads 44 and 45 to the cylindrical chamber 38.

The piston 34 is adjusted by means of a gearing, which 'consists principally of two levers 46 and 47 which are rotatable about pivots 48, 49 and carry at their free ends plungers 50 and 51, which can abut the outer ends of the piston 23. The two other ends of the levers, 46, 47 are connected together by means of a link 52 for simultaneous movement; moreover they abut the outwardly extending piston rods 53, Men the pistons 35 and 36.

The shaft 18 (Fig. 3) is connected by means of a link 55 to a disc 56 which resides loosely upon a shaft 57 and carries a pawl 58, the pawl engages in a ratchet wheel 59 situated rigidly upon the shaft 57. The shaft 57 contains further a pinion 60 which meshes with a pinion 61 upon a shaft 62. The latter is mounted in the slide 6, carries at its lower end .an eccentrical pivot 63 which has fixed on it a crank arm 64 connected with a toothed rod 66 by means of a pin 65. The toothed rod meshes with a pinion 67 upon a spindle 79 on which is located a worm wheel 68 which is in engagement with a worm 69. By rotating the worm 69, by means of the hand-wheel 8O fixed on the spindle 81 of the said worm 69, the rack rod 66 may be consequently moved and as this rod stands in communication with the shaft 62. this shaft 62, and also the entire slide 6 will be moved in the direction of the rack for being adjusted. If the worm 69 remains at rest and the shaft 62 on the contrary is turned, the excentric pin 63 effects a movement of the slide 6 in Fig. 3 towards the left or the right relatively to the not" ure 6 shows the position of the piston, as soon as the feed is ended. The piston in this instance has already assumed its right end position. Consequently it has brought the piston 34 into the position illustrated in Figure 6 by means of the lever 47. As a result of this, oil is now fed by the second pump 15 through the opening 37 upon the right side of the turning piston 39 (Figure 5). The turning piston consequently performs a rotation in an anti-clockwise direction and actually to an extent of about 90. During this movement the oil located upon the left side of the turning piston can flow through the openings 41 and 44. If the piston has reached its left end position then the opening 44 lies already somewhat at the right side of the piston 39. Both sides of the turning piston 39 are then connected through the cylinder chamber 33 with the outflow lead 42, the pump 15 then runs empty. a

The oscillatory movement of the piston 39 has also brought about a corresponding oscillatory movement of the disc 56 and this consequently has occasioned a rotation of the shafts 57 and 62 and therewith a small move ment of adjustment. As the piston 39 is rigidly connected to the shaft 18 the rotation of this piston about 90 simultaneously rotates the shaft .18 also about 90 so that the portion of this shaft constructed in the form of a three way cock is now turned through 90 to the position in Figure 4. The result of this is that the left side of the cylinder 22 stands in communication with the outflow opening 27 for the oil, while the oil fed fronr the pump 14 through the lead 16 and the and runs to the tank 83 again. This backwards rotation of the piston 39 results in a resetting of the three way cock of the shaft 18, which now again assumes the position shown in Figure 4, and the procedure is repeated-.

' stroke, and rotates the shaft 62 for a certain amount,- therefore effects a definite adjust--- ment. l The speed ofthe adjustment therefore depends simply upon the number of strokes of. the shaft 18 and a corresponding number of strokes of the piston 23. The number of strokes of the piston 23 is however again dependent upon what speed the pressure oil flows to one or other side of this piston since this speed through the throttle valve 1 7 may be regulated by correspondingadjustment of the-hand lever 30, there is reached, by means of the adjustment of the saidhand lever 30, a desired number of strokesof the piston 23 and consequentlya desired number of strokes of the entire gearing, and also of the. pawl 58. In other'words'the adjustment ofthe v cross-slide, thus the approaching of the work .tool to the work piece may be adj independently from of the machine,

usted quite the movement of the longitudinal slide. So long as the lever 30 preserves its position, the speed of adjustment depends upon the number of revolutions of the shaft 7, since this drives the oil pumps. In all cases therefore is there present a regulation of the stroke according to the speed of the slide.- -The faster the grinding disc rotates, the faster becomes the adjustment. Even then by the adjustment ofthe hand lever 30 a regulation corresponding to the diameter of the grinding disc, the quality of the grinding disc, the nature of the ma terial to be ground, may be undertaken. In every case by means of the adjustment ofthe hand lever 30 it maybe effected that for a' constant number of revolutions 'of the shaft 7 within a definite time there results a definite adjustment.

Of course the arrangementmay be carried out differently from the constructional point of view, thus one may choose, instead of the hydraulic drive illustrated and described in given cases also a mechanical drive, which,

issuing from the drive of the grinding disc or the tool, takes up them-ovement of the cross-slide independently from the movement; of the longitudinal slide. I claim: 1. An adjustment device particularly for the cross-slides of grinding machines comprising in combination with the cross 'slide a hydraulic piston for feeding the cross-slide, a pump serving for producing a medium under pressure moving said iston, a second hydraulic piston for controllng' said first-mentioned piston by leading the medium under pressure to the one or the other side of. the piston, a cylinder in which said second piston works, a second pump serving for producing a medium under pres- .sure'for moving said second piston, a pipe line leading thedriving medium to said cylof, a grinding inder, and a hand-controlled valve inserted into said hydraulic meansa-nd adapted to adjust same in accordance with. the time allowed for working.

2. An adjustment device particularly for the cross-slides of grinding machines comprising in combination with the cross-slide of the machine, a hydraulic piston for feeding the cross-slide, a pump serving for producing a medium under pressure for'moving said piston, a second hydraulic piston for controlling said first-mentionedpiston by leading the medium under pressure to the one or the other side of the piston, a cylinder in which said second piston operates, a second pump serving for producing a medium under pressure for moving said second piston, and controlling means controlling the medium driving said secondpiston. v v 3. An adjustment device particularly for the cross-slides of grinding machines comprising in combinationwith the cross-slide and the longitudinal slide'of the machine, a H hydraulic gearing for feeding the cross-slide,

hydraulic means for controlling said gearing,

and a hand-controlled valve inserted into said hydraulic means and adapted to adjust same in accordance with the time allowed for working said valve constituting also a safetyvalve. I

4. An adjustment device for the cross-slide machine, comprising in combination with the cross-slide a hydraulic system for feeding the cross-slide; a pump serving for producing a medium UJIdI pressure for driving said system; a second hydraulic system for controlling said first-mentioned Y hydraulic system; a second pump producing a medium under pressure for driving said second system; a grinding disc; means for' driving said disc and pumps in dependency of each other; and means inserted into' said second hydraulic system adapted to control the speed thereof at will during the opera-,

tion of the machine.

In testimony whereof I afiix my slgnature.

KARL JUN Gr. 

